Shock absorber



May 11, 1954 o. P. DE LOE SHOCK ABSORBER Filed July 3, 1952 3 Sheets-Sheet 1 'mmum i WWI INVENTOR. 0. Paul. OELQL m m BY umnu a fit:

0. P. DE LOE SHOCK ABSORBER May 11, 1954 3 Sheets-Sheet 2 Filed July 3, 1952 INVENTOR. 0. PAUL De Los May 11, 1954 o. P. DE LOE 2,678,115

SHOCK ABSORBER Filed July 3, 1952 3 Sheets-Sheet 3 ATTORNEY.

Patented May 11, 1954 sevens UNITED TNT OFFICE SHOCK ABSORBER Oliver Paul De Loe, Detroit, Mich.

Application July 3, 1952, Serial No. 297,029 10 Claims. (Cl. 188-89) This invention relates to shock absorbers and is a continuation in part of my copending patent application on a Shock Absorber, Serial Number 98,058, filed June 9, 1949, now United States Patent No. 2,605,861 dated August 5, 1952.

This present invention pertains to an improved shock absorber construction which is arrangedin conjunction with the vehicle suspension so as to offer a minimum resistance to vehicle spring deflection away from equilibrium and will provide a decreasing resistance to recoil as the suspension returns to equilibrium.

Vehicle springs are normally compressed by gravity so that the spring lift of a particular vehicle spring suspension and gravity are in exact equilibrium, which is the starting point of all spring movements.

Movement away from equilibrium is opposed either up or down by progressively increasin but yielding force with a zero resistance at equilibrium.

As the vehicle moves over any road irregularly, the springs yield an amount determined by inertia. Thus the yieldingis a concession to inertia more than to the road. But if the deflection is of suflicient duration the springs must accumulate SllfilClEllt strength to overcome inertia and deflect or turn the spring load as demanded by the road. This yielding accumulating force in the springs absorbs a large portion or the force of inertia thus delaying the deflection and convertin 2. rapid deflection into a more gentle curve.

When the accumulation of force by either spri "is or gravity has succeeded in deflecting the spring load so that it is again moving approximately parallel to the road, the full shock preventing function of the springs has been completed. This is accomplished efiectively without any other force or restriction. Any resistance added to the accumulating resistance of either springs or gravity will be opposing inertia unnecessarily, hastening deflection and contributing to shock.

Equilibrium must be restored. But if the accunmlated recoil force is permitted to make the return to equilibrium unchecked, it perpetuates deflection and sets up a series of oscillations, which are objectionable and frequently intensify subsequent deflections.

Recoil forces in springs are in direct proportion to the di. lance-from equilibrium, determined by spring characteristics, and can be measured by the gain or loss in springliit at anypoint. These recoil forces areprogressively diminishing to zero at equilibrium. Consequently, resistance to recoil 2 forces should also diminish as the recoil forces diminish with recoil forces retaining a suiiicient balance of power to insure complete return to equilibrium.

The relationship between recoil forces and resistance in the control device must be maintained while the vehicle is in motion and be re-established to meet the new equilibrium when the number of passengers or amount of cargo is changed.

It is therefore the object of the present invention to provide an improved and correct control for the spring suspension which will offer a minimum of resistance to primary movement away from equilibrium so that the same is not unnecessarily opposed.

It is the further object of this invention to provide improved shock absorber construction which will resist the recoil forces in proportion to the recoil forces but will permit complete return of the suspension to a point of equilibrium.

It is the further object of this invention to provide a decreasing resistance in the shock absorber corresponding to the diminishing recoil forces arriving at zero resistance to recoil slightly prior to equilibrium so that equilibrium will always have zero. resistance.

It is the still further object or this invention to provide a hydraulic shock absorber which utilizes fluid displacement by the primary movement of the suspension from equilibrium to activate the resistance necessary to effectively restrict recoil, i. c. the forces seeking to return the suspension to equilibrium.

It is the further object of this invention to utilize this initial fluid displacement for determining the amount of loading on a Spring loaded relief valve which is so designed that low fluid pressure will load the valve but would require a relatively high fluid pressure to open the valve.

These and other objects will be seen from the following specification and claims in conjunction with the appended drawings in which:

Fig. 1 is a top plan view of the shock absorber illustrating its connection fragmentarily with the vehicle spring suspension.

Fig. 2 is a section taken on line 22 of Fig.

Fig. 3 is a section taken on line 3-3 of Fig. 1.

Fig. 4 is a fragmentary elevational section sim ilar to Fig. 2 illustrating the relationship of the relief valve and other parts when the suspension is in equilibrium.

. is a similar view illustrating the relationship of the relief valve and other parts when the suspension is moving away from its position of equilibrium; and

Fig. 6 is a similar view of the relief valve and p rts in recoil resisting position.

It will he understood that the above drawings illustrate merely a preferred embodiment of the invention and that other embodiments are contemplated within the scope of the claims hereafter set forth.

Referring to the drawings, in Fig. 1 there is shown a shock absorber operating lever ll secured at its outer end to a portion of the vehicle suspension i2 by means of the transverse pin I3 and the cotter pins Iii. The opposite end H! of lever ii is immovably secured. over the splined or similarly formed outer end of the rocker shaft l5 which projects into shock absorber housing 2 I.

A pair of oppositely arranged sector shaped vanes ii and it are arranged upon the inner end of shaft and form a part thereof, their outer end surfaces being curved as at I 9 for sliding engagement with the circular interior surface of housing 2|.

There are also provided within housing 2| in spaced relation to vanes i? and i8, a pair of oppositely arranged similarly shaped stationary vanes 22 and 23 whose outer curved surfaces 39 snugly cooperate with the interior circular sur face Eli of said housing, and thereby provide the four chambers 24, 25, 26 and 27! within said housing into and from'which vanes i? and 58 are adapted to move upon movements of the spring suspension from its position of equilibrium.

Referring to Fig. 2, chambers and 2'5 are in communication with each other in view of the transverse passage 28 formed within the rock shaft 55 adjacent said vanes. Similarly, chambers 2d and 25 are interconnected by the second angularly related spaced passageway 29 formed in said rock shaft.

Referring to Figs. 2 and 3, the stationary vanes 22 and 23 positioned within housing 2i are secured upon one side of the circular plate 3! which has a hub 32 of reduced diameter, and within which is a circular recess 33 which houses the oil seal 35. Plate 3| is secured to housing 2i by the bolts 35 shown in Fig. 1.

Referring to Fig. 2, the upper portion 36 of housing 2i terminates in the interiorly threaded oppositely extending aligned portions 3'! and 38. Housing element 3% terminates at its upper end in the hollow extension 38', which is provided with a cover so defining the fluid or oil reservoir Q9, and is secured upon said housing by the bolts 4!.

. Cap 2 with annular exteriorly threaded portion it extends within housing extension 38 forming a closure therefore, and said cap is formed as a nut a l as in Fig. 1, to permit its adjustment within said housing extension.

Similarly, there is a second closure cap :35 with circular exteriorly threaded extension which threadedly engages within housing extension 3! and also hasan exterior nut formation 54, as shown in Fig. 1. V a

The upper portion of the housing El -36 has formed therethrough a central bore All in axial registry with caps 42 and 45 and the openings in housing extensions 37 and 3B. Hollow piston 48 with end wall 49 and central aperture 50 is reciprocaoly positioned within the bore 4'! upon one end thereof, and has an exterior shoulder 5i at its open end engageable with a portion of housing lit-for limiting the inward positioning thereof.

Coiled spring 52 is interposed between the in terior of cap 65 and end wall 69 of piston 38 and normally maintaining the same in the position shown in Fig. 2.

There is also provided a second similarly shaped oppositely arranged piston 53, open at one end and having an end wall E l at its other end, which is apertured at and which is also reciprocal within bore'd'l. The piston 53 also has an exterior shoulder-5S at its open end which engages housing limiting its inward positioning. A second coiled spring El is interposed between the interior of cap it and end wall 54 of piston 53 for normally maintaining said piston at its innermost position with respect to housing as illustrated in Fig. 2.

Passages 58 and 58 extend at their one ends into reservoir id and at their opposite ends are in communication with core El. Ball check valves are arranged in said passages and include the fittings so, the balls 6d normally closing off fluid communication through fittings as well as the coiled springs ill within said fittings which bear against said loalls.

Sliolably positioned contra within bore 57 intermediate pistons #23 and 5 is a control piston 62 centrally apertured at '33 to slidahly receive elongated check valve. Ed.

Said check valve has a central clone ted pas- 3a sage 55 throughout substantially length and terminates at its one end in passage ii of reduced diameter, which is adapted to permit equalization of low fluid pressures within the interior of bores ll when the device is held in any position, such as a position of equilibrium.

Control piston (52 also has formed therein at its opposite ends cylindrical openings within which circular plates and iii are slidahly movable in unison with movements of check valve 64. It will be noted that the plate 56 forms an integral part of valve upon one end thereof to facilitate assembly within control piston 32, and the second circular plate ill is secured upon the outside of check valve 8 by the turning over as at 68 of the end portions of said check valve. Consequently, control piston 62 and the relatively movable choc-.1 valve Ed with its circular end plates 66 and Ell, together form apart of the control unit for operation in the manner hereafter described.

Referring to Fig. 2, it is apparent that there are transverse outlets as and 'ie which are formed in the side walls of control piston adjacent their ends; and furthermore that the plates 53-5 and E? are adapted for control movements 1' tively to said outlets, such as illust .ted in as compared with the relative positioning of parts in Fig. 2.

The hollow portions at" within housing 3%, which communicate with the bore ii, are also in communication with the hollow portions ii and i2 into which fluid pressure is alternately transmitted by movement of the vanes ll and i3 through the ports 33 and E i.

Transverse openings "E5 in housing 38 provide a means of securing the shock absorber housing to the vehicle frame. Normally, for this purpose there are providedat least four such openings, two of which are illustrated in Fig.

Referring to Fig. 3, there is shown an annular opening 16 within the plate M in communication with the passage "El, and passage ii in turn cornmunicates with a registering passage '58 formed in the upper portion of housing 36 whereby excess oil seepage may be returned to reservoir sponse to movement of the vehicle away from position of equilibrium, it is conof control piston said fluid will be or through the communicating chambers 2 and 26. parent that upon such rotation of the vanes I'i mum comfort it is contemplated that the Operation sion' and with the shaft I5 it is, contemplated that such movements from equilibrium will eiiect rotary movements or rocking movements of the fluid moving means or vanes I! and iii with respect to the stationary vanes 22 and 23.

For illustration, assuming the movement of the suspension is such to cause a counterclockwise rotation of the vanes I? and i8 as indicatedby the arrow in Fig. 2, then in that case the fluid chamber 25 will be moved through port 13 into passageway H due to the pressure exerted upon it by the moving vanes il and it inasmuch as chambers 25 and 27 are interoon nected by passageway 23.

Fluid in passageway ll can pass through the space between control piston 62 and piston and also through port it of control piston 52.. In view of the aperture in piston the pressure of the fluid in passageway ii be transmitted to the interior of piston 53, however it is apparent that said piston will remain stationary. As the fluid passing through port was well between the pistons 62 and will be upon opposite sides of the check valve plate or control piston iii, it is apparent that the net moving force of fluid upon piston 52 will he throughout the cross-sectional area of check' valve 5t and will cause control piston 52 to move to the left shown in Fig. 5.

left in resuspension Ascont ol piston t2 moves to the temple-ted as an important part of the present invention, there be a minimum resistance to the displacement of the fluid upon the left side t2. directed through passageway 52 from either between piston E2 and piston ports so that as indicated by the arrow in i 5, the displaced fluid will he moved with a minimum of resistance through passageway "it and into the central chamber or It is ap and i8 chambers 25 and 2? will be reduced It is contemplated furthermore as an important part of the present invention that this rela tively freemovement away from equilibrium vill bebuilding up the forces which will eventually retard or restrict the return flow of fluid through.

passageway 12 as the suspension returns to. its position of equilib 'ium.

To avoid shock and to provide for the maxirecoil of the suspension back to its position of equilib mum will be yieldably resisted with a decreasing force-as said suspension returns to equilibrium sothat just prior tot-he return to equilibrium,

the force will bezero.

' This is accomplished in the present constru it is contemplated that.

out the; purposes of th providing a minimum resistance tomovement of tion by the compression of the spring 52 within the moved piston 58. While piston $2 is spaced from piston 43 in Figs. 2 and 4, it is apparent from Fig. 5 that on movement to the left control iston 52 engages piston 33 so that piston 58 is moved to the left as in Fig. 5 from the neutral position shown in Figs. 2 and 4:. This move-- ment has gradually compressed spring 52 to thereby provide an increased pressure contact of piston 53 with control piston {52; the fluid, however, will flow through ports 6% and also through port ill into chamber 2 5. Fig. 5 lustrates therefore the relationship of the moved piston 53 the control piston 62 with respect to the valve B l.

As piston S2 moves to the left there may also be some flow betwee the end of piston 62 and moved piston it, however, this flow through passageway i2 is with minimum or restriction.

Upon completion of the movement of the suspension away from eouilibriiun vanes I? and it will have stopped moving. The recoil of the spring suspension tending to return the same to itsposition of equilibrium will produce a clockwise. rotation of the moving elements or vanes l! and i reducing the size of charmbers and 2t and increasing the of chamo. one of the ports so closing off the passage of low to the between pistons and 48.

Referring to Eig. 6, it will be seen that the diameter of piston G3 is slightly greater than the meter of the left end portion of control piston 5'52 to thereby define an annular pressure area it?! against which return. iiow of fluid can act tending to move pi ton .8 to the left of piston providing the space thereoetween shown in 8. This will permit the flow of return fluidinto the between pistons t3 and iii? so as to a return movement to the right of piston corresponding to the restricted return of the suspension back to its position of equilibrium.

Thus the present .iechanisin provides a yield.- in resistance to reverse flow of fluid to thereby control e recoil of the vehicle suspension. It is apparent that as the piston {iii moves to the right, the compression of spring F will be gradually consequently the pressure Contact between pistons d will he reduced so that there is a 'ng resistance to this return new of fluid between piston t2 and piston 53.

this yielding resistalmost IJ". urnerl to its neutral position at which time the reel Zero as parts will have assumed a rel to position as shown in Figs. 2 and 4-. It is contemplated as an essential part of present invention this yielding resistance to the return flow of be to be fore the control piston well t. vehicle suspension has reached position of eouil-hiillll'l so that at sol b .111 there is zero once to movement of the suspension away from the position of equilibrium.

Thus, the apparatus above dear. 1 carries present invention in the vehicle suspension away from its position of equilibrium. However, the flow of fluid during this movement is adaped to build up the forces which will control and yieldably restrict the recoil of the vehicle suspension when it returns to equilibrium. It is furthermore contemplated that this yielding resistance or control of the recoil will be gradually reduced, it is apparent from Figs. 2 and i that t -e compression in spring 52 is gradually reduced as the control piston 52 goes to the right.

The reverse operation takes place if the initial deflection of the suspension from equilibrium is in the opposite direction from that above described as this will cause a clockwise rotary movement of the fluid moving means or vanes I? and 13.

In this case fluid will be moved under pressure through port is and passageway l2 causing movement to the right of control piston 62, and a similar spring compressing movement of piston 53. Flow on the opposite side of control piston 62 will pass through port ill, passageway l l and port 13 into chamber 25; and this flow will be relatively unobstructed. Upon the return of the suspension towards equilibrium, the flow is reversed, but now there is provided a yielding resistance to the return flow due to the pressure of contact between the control piston 62 and piston 53. difference in diameter between piston 62 and piston as to provide an annular pressure area on piston 53 which corresponds to the pressure area is shown in Figs. and 6, but which will then be upon the opposite side of control piston 52.

In the manner above described, it is apparent also that the recoil of the suspension is thereby controlled and yieldably restricted and furthermore that this resistance gradually decreases as does the compression in spring ill upon the return movement of control piston 62 towards its central position. Furthermore this resistance will be zero prior to return of the suspension to equilibrium, for the same reasons above given.

. Having described my invention, reference should now be had to the claims which follow for determining the scope thereof.

I claim:

1. In a hydraulic shock absorber having a housing and a rockable fluid moving means therein joined to the spring suspension of a vehicle, said housing being formed with a central fluid chamber for said fluid moving means and a transverse bore forming a pair of spaced opposed cylinders, and with two fluid passages respectively connecting the central chamber with said cylinders, an apertured reciprocal recoil control piston within each cylinder, a spring in each cylinder normally urging said pistons toward each other, said fluid moving means adapted to alternately direct fluid into one of said passages on movement of said suspension in one direction away from equilibrium, a control piston in said bore spaced intermediate said pistons, and a fluid flow restrictor valve adjustably movable within said control piston, said restrictor valve being longitudinally apertured, said control piston being adapted for longitudinal movement responsive to the fluid in said one passage freely displacing fluid through the other passage to said central chamber and operatively engaging and moving the piston corresponding to said other passage compressing its spring to increase the contact pressure of said control piston with said moved piston, the diameter of said control Of course, there will be the same piston being less than the diameter of said moved piston thereby defining an overlapping pressure area responsive to and yieldably resisting the reverse flow of fluid in said second passage on return of said suspension towards equilibrium in proportion to the compression of the spring bearing on said moved piston.

2. In a hydraulic shock absorber having a housing and a rockable fluid moving means therein joined to the spring suspension of a vehicle, said housing being formed with a central fluid chamber for said fluid moving means and a transverse bore forming a pair of spaced opposed cylinders, and with two fluid passages respectively connecting the central chamber with said cylinders, an apertured reciprocal recoil control piston within each cylinder, a spring in each cylinder normally urging said pistons toward each othensaid fluid moving means adapted to alternately direct fluid into one of said passages on movement of said suspension in one direction away from equilibrium, a control piston in said bore spaced intermediate said pistons, and a fluid flow restrictor valve adiustably movable within said control piston, said control piston being adapted for longitudinal movement responsive to the fluid in said one passage freely displacing fluid through the other passage to said central chamber and operatively engaging and moving the piston corresponding to said other passage compressing its spring to increase the contact pressure of said control piston with said moved piston, the diameter of said control piston being less than the diameter of said moved piston thereby defining an overlapping pressure area responsive to and yieldably resisting the reverse flow of fluid in said second passage on return of said suspension towards equilibrium in proportion to the compression of the spring bearing on said moved piston, said restrictor valve having a restricted longitudinal passage therethrough for equalizing the pressure on opposite sides of said control piston while said suspension is in a position of equilibrium corresponding to a particular load.

3. In a hydraulic shock absorber having a housing and a rockable fluid moving means therein joined to the spring suspension of a vehicle, said housing being formed with a central fluid chamber for said fluid moving means and a transverse bore forming a pair of spaced opposed cylinders, and with two fluid passages respectively connecting the central chamber with said cylinders, an apertured reciprocal recoil control piston within each cylinder, a spring in each cylinder normally urging said pistons toward each other, said fluid moving means adapted to alternately direct fluid into one of said passages on movement of said suspension in one direction away from equilibrium, a control piston in said bore spaced intermediate said pistons, a fluid flow restrictor valve adjustably movable within said control piston, said restrictor valve being longitudinally apertured to permit a balance of fluid pressure in said cylinders when said suspension is in equilibrium, said control piston being adapted for longitudinal movement responsive to thefiuid in said one passage freely displacing fluid through the other passage to said central chamber and operatively engaging and moving the piston corresponding to said other passage compressing its spring to increase the contact pressure of said control piston with said moved piston, the diameter of said control piston being less than the diameter of said moved piston thereby defining an overlapping pressure area responsive to and yieldably resisting the reverse flow of fluid in said second passage on return of saidsuspension towards equilibrium in proportion to the compression of the spring bearing on said moved piston, said control piston having aligned cylindrical openings at its opposite endsand lateral fluid ports in the piston walls joining said openings, and spaced control pistons on opposite ends of said restrictor valve movable within saidcylindrical openings for controlling the flow of fluid to and from said passages through said ports.

4. In a hydraulic shock absorber having a housing and a rockable fluid moving means there-- in joined to the spring suspension of a vehicle, said housing. being formed with a central fluid chamber for said fluid moving meansrand a trans-- verse bore forming a pair of spaced opposedcylinders, and with two fluid passages respectively connecting the central chamber with said cylinders, an apertured reciprocal recoil control piston within each cylinder, a spring in each; cylinder normally urging said pistons toward each other, said fluid moving means adapted to alternately direct fluid into one of said passages on movement of said suspension in one direction away from equilibrium, a control piston in said bore spaced intermediate said pistons, and a fluid flow restrictor valve adjustably movable within said control piston, said restrictor valve being longitudinally apertured to permit a balance of fluid pressure in said cylinders when said suspension is in equilibrium, said control piston being adapted for longitudinal movement responsive to the fluid in said one passage freely dis-* placing fluid through the other passage to said central chamber and operatively engaging and moving the: piston corresponding to said other passage. compressing its spring to increase the contact pressure of said control piston with said moved piston, the diameter of said control pis-- ton being less than the diameter of said moved piston thereby defining an overlapping pressure area responsive to and yieldably resisting; thereverse flow of fluid: in said second passage on re-- turn of said suspension towards equilibrium in proportion to the compression of thespring bearing on said movedpiston, said fluid moving means being adapted to direct fluid into the other oi said passages on movement, of said suspension in the opposite direction away from equilibrium.

5. In a hydraulic shock absorber having a: housing and a rockable fluid moving meanstherein joined to the spring suspension of a vehicle;

said housing being formed with a central fluidchamber for said fluidmoving means and a transverse bore forming a pair of spaced opposed cylinders, and with two fluid passages respectively connecting the central chamber with said cylinders, an apertured reciprocal recoil control piston within each cylinder, a spring in each cylinder normally urging said pistons toward each other, said fluid moving means adapted to alternately direct fluid into one of said passages on movement of said suspension in one direction away from equilibrium, a control piston in said bore spaced intermediate said pistons, a fluid flow restrictor valve adjustably movable within said control piston, said control piston being adapted for longitudinal movement responsive to the fluid in said one passage freely displacing fluid through the other passage to said central chamber and operatively engaging and moving the piston corresponding to said other passage compressing its spring to increase the contact pressure of said control piston with said moved piston, the diameter of said control piston being less than the diameter of said moved. piston thereby defining an overlapping pressure area responsive to and yieldably resisting the reverse flow of fluid in said second passage on return of said suspension towards equilibrium in proportion to the compression of the spring bearing on said moved piston, and caps threaded into the opposite outer ends of said bore for closing said cylinders and for regulating the initial compression of said springs.

6. In a hydraulic shock absorber having a housing and a rockable fluid moving means therein joined to the spring suspension of a vehicle, said housing being formed with a central fluid chamber for said fluid moving means and a transverse bore forming a pair of spaced opposed cylinders, and with two fluid passages respectively connecting the central chamber with said cylinders, an apertured reciprocal recoil control piston within each cylinder, a spring in each cylinder normally urging said pistons toward each other, said fluid, moving means adapted to alternately direct fluid into one of said passages on movement of said suspension in one direction away from equilibrium, a control piston in said bore spaced intermediate said pistons, and a fluid flow restrictor valve adjustably movable within said control piston, said control piston being adapted for longitudinal movement responsive to the fluid in said one passage freely displacing fluid through the other passage to said central chamber and operatively engaging and proportionto the compression of the spring bearing on saidmoved piston, the reverse flow in said second passage gradually returning said control piston to its initial central position thereby reducing the compression of said spring on said moved piston so as to gradually decrease the resistance to said return flow resulting in a gradually decreasing resistance to recoil of said suspension back to equilibrium.

'7. In a hydraulic shock absorber having a housing and a rockable fluid moving means therein joined to the spring suspension or a vehicle, said housing being formed with a central fluid chamber for said fluid moving means and a transverse bore forming a pair of spaced opposed cylinders; and with two fluid passages respectivelyconnecting the central chamber with said eylinderaan aperturedreciprocal recoil control piston within each cylinder, a spring in each cylinder normally urging said pistons toward each other, said fluid moving means adapted.- toalternately direct fluid into one of said. passageson movement of said suspension in! ll engaging and moving the piston corresponding to said other passage compressing its spring to increase the contact pressure of said control piston with said moved piston, the diameter of said control piston being less than the diameter of said moved piston thereby defining an overlapping pressure area responsive to and yieldably resisting of the reverse flow of fluid in said second passage on return of said suspension towards equilibrium in proportion to the compression of the spring bearing on said moved piston, and a pair of spaced opposed stationary vanes in said central fluid chamber, said fluid moving means including a pair of oppositely directed vanes spaced from said first vanes and adapted on rotary movement to effect flow through said passages from and to said central chamber.

8. In a hydraulic shock absorber having a housing and a rockable fluid moving means therein joined to the spring suspension of a vehicle, said housing being formed with a central fluid chamber for said fluid moving means and a transverse bore forming a pair of spaced opposed cylinders, and with two fluid passages respectively connecting the central chamber with said cylinders, an apertured reciprocal recoil control piston within each cylinder, a spring in each cylinder normally urging said pistons toward each other, said fluid moving means adapted to alternately direct fluid into one of said passages on movement of said suspension in one direction away from equilibrium, a control piston in said bore spaced intermediate said pistons, a fluid flow restrictor valve adjustably movable within said control piston, said control piston being adapted for longitudinal movement responsive to the fluid in said one passage freely displacing fluid through the other passage to said central chamber and operatively engaging and moving the piston corresponding to said other passage compressing its spring to increase the contact pressure of said control piston with said moved piston, the diameter of said control piston being less than the diameter of said moved piston thereby defining an overlapping pressure area responsive to and yieldably resisting the reverse flow of fluid in said second passage on return of said suspension towards equilibrium in proportion to the compression of the spring bearing on said moved piston, said fluid moving means including a shaft projecting from said housing, and a lever joined at one end to said shaft and joined at its other end to said suspension.

9. In a hydraulic shock absorber having a housing and fluid moving means therein joined to the spring suspension of a vehicle, said housing being formed with a fluid. chamber for said fluid moving means, a second fluid chamber, and fluid passageways interconnecting portions of said first chamber with two spaced portions of said second fluid chamber, a movable fluid flow restrictor valve control element in said second chamber responsive to the flow in one direction from said first chamber through one of said pas- 6 sageways upon movement of said suspension from equilibrium, and with a substantially non-restricted flow of fluid through the other passageway back to said first chamber, a secondary control means engageable by said control element and movably responsive to its movement, and a compressive element retainingly engaging said secondary control means, whereby upon movement of said restrictor valve control element, said compressive element is compressed so that said secondary control means compressively engages said restrictor valve control element, building up a force between said restrictor valve control element and said secondary control means to yieldably and decreasingly restrict the return secondary flow of fluid through said second passageway as said suspension returns to its initial position of equilibrium, whereby fluid displacement by primary movement of said suspension actuates the resistance necessary to restrict secondary flow of fluid to efiectively restrict recoil of said suspension back to equilibrium.

10. In a hydraulic shock absorber having a housing and a rockable fluid moving means therein joined to the spring suspension of a vehicle, said housing being formed with a central fluid chamber for said fluid moving means and a transverse bore forming a pair of spaced opposed cylinders, and with two fluid assages respectively connecting the central chamber with said cylinders, an apertured reciprocal recoil control piston within each cylinder, a spring in each cylinder normally urging said pistons toward each other, said fluid moving means adapted to alternately direct fluid into one of said passages on movement of said suspension in one direction away from equilibrium, a control piston in said bore spaced intermediate said pistons, and a fluid flow restrictor valve adjust ably movable within said control piston, said control piston being adapted for longitudinal movement responsive to the fluid in said one passage freely displacing fluid through the other passage to said central chamber and operatively engaging and moving the piston corresponding to said other passage compressing its spring to increase the contact pressure of said control piston with said moved piston, the diameter of said control piston being less than the diameter of References Cited in the file of this patent V UNITED STATES PATENTS Number Name Date 2,559,968 Katz July 10, 1951 2,604,953 Campbell July 29, 1952 De Loe Aug. 5, 1952 

